Roll grinding machine



June 8, 1965 Filed 0612. 8, 1963 R. GRZYMEK ROLL GRINDING MACHINE 8 Sheets-Sheet l INVENTOR ROLF GRZYMEK AT RNEYS June 8, 1965 R. GRZYMEK ROLL GRINDING MACHINE 8 Sheets-Sheet 2 Filed Oct. 8, 1965 June 8, 1965 R. GRZYMEK ROLL GRINDING MACHINE 8 Sheets-Sheet 3 Filed OO'. 8, 1963 W 'lv U q m June 8, 1965 R. GRZYMEK 3187468 ROLL GRINDING MACHINE Filed Oct. 8, 1983 8 shees-sheet 4 /l' Nmf m.

June 8, 1965 R. GRzYMEK 3,187,468

ROLL GRINDING MACHINE Filed Oct. 8, 1963 8 Sheets-Sheet 5 June 8, 1965 R. GRZYMEK ROLL GRINDING MACHINE 8 Sheets-Shee'c 7 Filed 00t- 8, 1963 mar United States PatentO p o ROLLGRINDING MACHINE `Rolf Grzymek, Cincinnati, Ohio, assignor to The. Cincinnati `Milling Machine Co., Cincinnati, hio, a corporatiou of Ohio i FiledOct. 8, 1963, Ser. No. 314,703

'15"Claims, (Cl. 51-49) This invention relates to roll grinding machines and more particularly to a `compound feed mechanism for` movement of aV grinding wheel to grind selected cambered r'oll sha'pes..

t Itis necessary to grind the rolls `of metal rolling mill stands and rollssuch as forpaper calendar stacks with a slight cambered profile.` Income cases this profile is convex and inother cases the profile is concave.V These shapes are found on rolls of varying lengths throughout a mill. Therefore a cambering mechanism for producing them should be adaptable to produce any selected shape of a wide variety of cambered shapes. Since the amount of camiber is usually only a few thousandths of anzinch, even on very long rolls the mechanism producing it must be very. accurate and smooth-ly operable as well as versatile. Various mechanisms have been used to v provide .a component of grinding wheel feed toward and away-'from a roll in .timed relation With the progress of the grinding wheel along theroll to produce the proper cambered shape. i However, the mechanisms availableV heretofore have been inconvenient to VVreset' when the size or profile shape of `a roll to beground is different from that of the roll previous-ly ground. Since these machines are necessarily large, any mechanismwhich requires the f operator's movement around the machine and on and off of it is less desirable than a machine in which a change in camber, ca'n be madeat a single location without movement around the machine.. This is particularly true since a roll grinder is'seldom used'in a single lset-up to grind in succes'sion atnumber of identical roll profiles and therefore the redulctioniof set-up time is important.

. 'Camber mechanismsheretofore have required that .the operator leavehisfnormal `Operating station to make camber changes and thus have required movements around the ma'cihne that result in long set-upprocedures.

'It isttherefore an objectof this invention to provide an improved roll grindingmachine in .which'there is a more convenient feed mechanism=-including` a cambering mechanism allowingfor a quick and convenient change to producea desired'roll profile. f t r. 1

It is also an object of this invention to provide a roll grindingmachine in which a camber change can be made bythe machine operator while he'rernains at'his normal Operating station.

It is a further` object of this invention to provide a mechanism for setting camber in which .the amount of camber can be read directly from a camber setting diial:

ICC

head that is tiltableabout one end to swing a grinding wheel carried thereby toward and away from a roll to be ground. The cam rests upon a roller which in turn is supported by av Wedge that is reciprocally movable thereunder to produce lifting and lowering of the wheelhead to tilt the grinding wheel in a reversible fine feed movement. A mechanism is included to rotate the cam Asimultaneously with and in response to 'relative movement of the grinding wheel along the roll to provide a component of feed independent of the fine 'feed to produce a cambered shape on the roll. This' mechanism includes a motor connected to the cam and a control circuit to energize the motor to rotate the cam an amount corresponding to the relativeV movement of the grinding wheel along the roll. This rotation of the cam produces the carubering feed component due to the eccentricty of the cam about its axis of rotation. i The eccentricity of the cam is adjustable inresponse to the rotation of a dial -linked thereto and thev dial is'calibrated directly in terms of the amount of camber to be produced for any angular setting of the dial. V The camber to be produced may be either concave or convex on the roll and the control circuit energizing the cam motor includes means by which the cam is selectively adjusted by operation ofthe a motor to align the cam initial'ly to'produce either the concave or the convex roll Shape. The axis on `which the cam rotates is parallel to the aXis of the grinding Wheel spindle in the preferred Vmachine and the Wedge is movable ina direction perpendicular to lthese axes thus eliminatingiside thrusts on the wheelhead during both the fine feed and cambering feed movements.

A clear understanding of the construction and operation of the roll grinder of this invention can be obtained from the following detailed description in` which reference is made to the attached drawings wherein:

|FIG. VV1 is an end view of a traveling'wheelhead roll grinder withlt'he control cabine-t along side the operatofs station on the whee'lhead carriage omitted to expo`se the side of the wheelhead.

FIG. 2 .is a diagram showing a roll having gerated camber for purposes of illustration.

'F1G. 3 is a diagrammatic representation of a portion of the feed mechanismV Z FIG. 4 is a. diagrarnmatic showing of the wheelhead feed mechanism. w

PIG. 5 'is a simplifiedV section of the feed meohanism all eXag-f with a schematic showing ofrthe feedcontrol circuits.

shouldbe readily apparenttby reference -to the followi ing specification, considered in conjunction with the accompanying drawings forming a part thereof, and it is to be understood .that any modifications may be made in theexact structural detailspthere .shown and described,

withinthe scope of the appended claims, Without depart-` ing from or e'xceeding the spirit o f the-invention.

`In its preferred' form, a 'roll grinder constnrcted in accordance with the teaching of this invention has an eccentrically rotatable-cam-bering feed cam in a Wheel- FIG. 6 is a cro'ss section of the wheel'head of-the machine of FIG. 1, on line 6-6 thereof. FIG. 7 is a section. of the wheelhead on line V7---7 of FIG.6., g .l' 'N i FIG. 8. is a section of the w'heelhead 'on line 8-8 of FIG. 7.

FIGS. 9 and 10 are schematic hydraulic circuit diagrarns for the operation of the feed' mechanism of the grinding machine of PIG. i

FIG. 11 is a schematic electrical control circuit for the machine o f FIG. 1 with the hydraulic circuit of FIGS. 9 and 10. v i

FIG. 12 is avpartial plan view of the mechanism as viewed from line 12-12 of FIG. 6.

The roll 'grindingpmachine shown in FIG. lis a traveli ling wheelhead type in which a roll 15 to be ground isV rotatably supported at a fixed position by a headstock 16 plies the power to rotate the roll 15. A rear bed 22 is attached to the front bed 19 by structural members 23 and is rigidly supported parallel to the front bed 19 b Patented June 8, 1965 the floor 20. Longitudinal ways 24, 25 are formed on the top of the rear bed 22 and extend along its length parallel to the work supporting ways 17, 18. A carriage 26 is slidably received on the ways 24, 25 for movement therealong parallel to the aXis of the roll 15. A` swivel plate 27 is received on top of the carriage 26 for angular adjustment about a trunnion 28. The swivel plate 27 has ways 29, 30 formed on its top to receive a slide member 31 for movement along the ways 29, 30. The ways 29, 30 areused during the grinding of tapered necks on the roll and in such an operation the ways 29, 30 are not parallel to the ways 24, 25. In normal grinding of a roll, the swivel plate 27 is angularly positioned and clamped so that the ways 29, 30 are parallel to the ways 24, and the slide member 31 is clamped at a fixed location on the ways 29, while the carriage 26 is reciprocally moved along the ways 24, 25. Other ways 32, 33 (see FIG. 6) are formed on top of the slide member 31 perpendicular to the ways 29, 30 and a wheelhead slide V34 is received thereon for coarse reciprocal positoning movement thereof toward and away from the roll 15.

A wheelhead 35 is received on top of the slide 34 and,

is pivotally attached at its forward end to a trunnion 36 that is perpendicular to the ways 32, 33. The rear end of the wheelhead 35 can be raised and lowered relative to the wheelhead slide 34 to swing a grinding wheel 37 in an arc around the trunnion 36 toward and away from the roll 15 in both a fine feed motion and a cambering feed motion by a mechanism now to be described in detal.

FIG. 4 shows in a simplified manner the basic elements of the compound feed mechanism utilized to tilt the wheelhead 35 and swing the grinding wheel 37 around the trunnion 36for both fine feed and cambering feed. FIG. 4 also reveals that the wheelhead slide 34 is movable on the slide member 31 by the operation of a motor 38 that rotates a screw 39 which is threadedly engaged through a depending nut 40 integral with the wheelhead slide 34. The compound feed mechanism is 'comprised of a circular cam 41 that is rotatably carried in the wheelhead 35 on an eccentric axis 42. The rear of the wheelhead 35 is supported by a wedge 43 which is reciprocally movable along the wheelhead slide 34 on rollers 44. Interposed between the wedge 43 and the cam 41 is a roller 45. The wedge 43 is moved by a geared drive from a handwheel 46 (FIG. 1) and including a pinion .47 fixed to rotate with the hand wheel 46, gears 48, 49, 50, 51, 52 and a screw 53 and rotatable nut 54. It can be seen from FIG. 4 that either the rotation of the cam 41 on the eccentric axis 42 or the movement of the wedge 43 will produce a lifting or lowering of the rear of the wheelhead 35 to swing the grinding wheel 37 around the trunnon 36.

The detailed construction of the compound feed mechanism in the preferred embodiment is shown in the wheelhead section views of FIGS. 6, 7, and 8.- The cam 41 is attached to a shaft 55 which is journalled for rotation in bearings 56,57 in the wheelhead 35,. The cam 41 is adjustable on the end of the shaft 55 to'be eccentric relative to the axis thereof. Therefore the cam 41 has a tongue portion 58, FIG. 8, .which extends across its backside and is fitted in a corresponding slot 59 that is across a flange portion 60 on the end of the shaft 55. The tongue portion 58 has a slot 61 thereacross in which a pair of cam members 62, 63, FIGS. 6, 7 are fixed securely by pins 64 and screws 65. A clearance hole 66 is formed through the center of the cam 41 and the'end of an adjusting rod 67 extends loosely therethrough. The rod 67 has tapered and parallel surfaces 68, 69 on opposite sides thereof which are engaged by the cam members 62, 63 respectively. The rod 67 is axially adjustable when the cam 41 is loosened on the shaft 55 and the coaction of the surfaces 68, 69 is to bear against the cam members 62, 63 to produce lateral forces to shift the cam 41 in accordance with the direction and amount of movement of the rod 67.

As shown in FIG. 6, the rod 67 is slidably received through an axial opening 70 in the shaft 55. The end of the shaft 55 opposite the cam 41 has a multi-diameter recess therein in which a threaded bushing 71 is fixed by screws 72. A threaded ring 73 is received behind the bushing 71 and held therein by screws 74 and jack screws 75 at a selected distance from the bushing 71. A threaded shaft 76 is engaged through the'bushing 71 and ring 73 and is rotatable in one direction and the other to axially shift the rod 67. The spacing of the bushing 71 and ring 73 is such that backlash is eliminated when the shaft 76 is reversibly rotated. The shaft 76 is rotated by means of a handcrank 77 removably received in the outer end of the shaft 76 by means of a drive socket. A dial 78 is fixed by means of a pin 79 to rotate with the shaft 76. The dial 78 carries a pinion 80 which is orbital with the shaft 76 and is in mesh with two internal toothed ring gears 81, 82. The gear 81 is fixed to a member 83 by means of screws 84 and the member 83 is fixed to the shaft 55 bypscrews 85 (shown out of position). At the time the handcrank 77 is used, the shaft 55 is prevented from rotating as will he described subsequently. The gear 82 is loosely received over the outer diameter of the gear 81 and is rotatable relative thereto. The gears 81, 82 have a slight difference in their number of teeth so that Vas the shaft 76 is rotated and the pinion 79 is swung around, the gear 82 is caused to' rotate slowly over the gear 81 which is stationary at this time. A thin collar 86 is fixed over the outer surface of the member 83 and an aperture 87 is formed therein to view the outer peripheral surface of' the gear 82. AS shown in FIG. 12 the collar 86 has alreference mark 87' scribed thereon and the dial 78 and gear 82 have calibration marks 88, 89, respectively therearound. These calibration markings 88, 89 enable the machine operator to read directly the amount of eccentricity of the cam 41 in terms of the height or depth of camber which the cambering feed Will produce for anygiven adjustment. The markings 89 on the gear 82 give a coarse reading while the dial markings 88 provide a vernier scale reading since the gear 82 is rotated at a much slower rate than the dial 78.

The cam 41 can also be locked in place on the shaft 55 once it has been set to a selected eccentricity by the described mechanism. A pair of looking bars 90, 91 extend |axially through the Ashaft -55 on eith'er side thereof (the bar 90 is shown ninety degrees out of position in FIG. 6). Each of the bars 90, 91 is similar to the other in construction and operation. As shown, a cap 92 is threaded onto the end of the bar 90 beyond the cam 41 and locked in place by a set screw 93. A ring 94 is fixed onto the bar 90 in the shaft 55 and a spring 95 bears against the ring 94 and constantly urges the bar 90 to- Ward the right as viewed in FIG. 6. A pin 96 extends through the shaft 55 and into the vbar 90 to prevent it from rotating while Vallowing limited axial movement. The other end of the bar 90 is threaded toreceive a socket 97 which is rotatable i-n the member 83.`l An opening 98 through the collar 86 and a notch 99'in the member 83 provides acess -to the socket 97 so that the operator can turn it when it is desred either to release or to clamp the cam 41 on the shaft 55. Rotation of the socket 97 in one direction will force the ibar 90 to the left against the spring 95 which Vunclarnps the cam 41. Rotation of the socket 97 in the other direction moves the bar- 90 so that a clamping force is provided from the cap 92 bearing on the cam 41 and the socket 97 bearing in thel member 83 to hold the cam 41 firmly in an adjusted position on the shaft 55. As shown in FIG. 7, the cam 41 has elongated openings 100, 101 through which the bars 90, pass to allow a wide range of adjustment of the cam The wedge 43 is shown in detal in FIGS. 6 and 7. A track member 102 is fixed on the top of the wheelhead slide 34 and a plurality of sets of recirculating roller bearing shoes 103 are attached to the bottom of the wedge of the screw 53'through the nut 54.

43 with the rollers `104 therein in d'irect rolling contact with the track 102. Extending upward from the track 102 on each side'of the wedge are a pair of roller supports 105, 106 each of which has a roller 107, 108 on top that bears againsta side of the Wedge 43 such that it is held in central alignment on the track 102 as it is shifted. The forward end if the Wedge 43 has a coupling shaft 109 attached thereto by a stud 110 which is fixed at opposite ends between the wedge 43 and shaft 109 by pins 111, 112. The screw 53 is attached to the other end of the shaft 109 by a pin 113. The screw 53, as shown in FIG. 7 in its preferred form, is an antifriction ball bearing screw and the nut 54 engaged therewith is a recirculating ball typenut. As shown, the nut 54 is fixed to the gear 52 by screws 114 and the nut 54 and gear 52 are rotatable together in a support 115 which includes anti-friction bearings 116, 117and which is attached to the slide 34. The gear 51 is also rotatable in the support 115, it being integral with a short shaft 118 that is received in bearings 119, 120 in a bushing 121 that is fixed in the support 115. The rotary drive from the handwheel 46 (FIG. 1) includes two knuckles 122, 123 at each end of a shaft 124 in the drive train lto the gear '51 since the handwheel 46 is journaled in the wheelhead 35 which tilts relative to 'the' slide 34 to which the support 115 is fixed. The knuckles 122, 123 provide the flexibility in the drive train which allows the handwheel 46 to move relative to the support 1'15 lin which the gear 51 is journalled. A stop member r1-25, 1126 is fixed at each end of the screw 53 to provide positive limits for the travel The roller assembly 45 which bears between the wedge 43 and cam 41 is also shown in detailV in FIGS. 6Vand 7. The'roller assembly 45 is comprsed of a pair of rollers 127, 128 and a third roller 129 received therebetween. Each of the rollers 127, 128, 129 is rotatably received on needle bearings 130 that are carried on an axle 131. The top of the wedge 43 has arecess 132 therealong so that the roller 129 which is slightly larger than the rollers 127, 128 bears against the cam 41 but not the wedge 43. The rollers 127, 128`engage the wedge 43 on either side of the -recess 132 but, 'being smaller than the rollerv129, they do not engage the cam 41. By this construction, the cam 41 may be-rotated while the wedge 43.is` moved along the track 1102 and these movements can be 'made simultaneously without adverse friction loads to prevent them since all contacts are made at rolling surfaces. The axle 131 is received at one Vend of a 'bracket 133 which straddles the screw`53 at its other end and is pivotally' attached to 1a journal member `134 fixed ltoithe slide S4 at a point spaced both from the cam 41 and wedge 43.

vThus as the wedge43 is moved along the track 102, the

roller assembly 45 is swung' about a center spaced from the cam 41 and wedge 43.

The diagramaticfviews of FIGS. 2 and 3 illustrate the importance of 'swinging the roller assembly 45 when the Wedge 43 is shifted. The .convex cambered shape of the rolll 15 is shown in FIG. 2.` 'In starting a grinding operaton to produc'eV this roll Shape, the grinding wheel 37 (PIG. 1) is ali'gned at the lcenter of the roll 15 and the cam 41 is rotated to have its least eccentric surface bear- 'ing against the roller assernlbly 45. The roller 45 also bears on the wedge 43 as shown. During the grinding operation, the Wedge is movedrightward to produce fine feed and can be shifted to the position indicated at 135. A corresponding rise of the' roller 45 to the position 136 would occur if the roller moved only vertically. The roller 45 however should be .at the :position 137 if it'is to en- Since the cam 41 is rotated in timed relation with move- Inent of the grinding wheel 37 alongthe roll 15, the highest point in the crown of the cambe'red roll would then be off-set from the center of the roll 15 and the low points of the crown would not occur at the ends` of the roll. An exaggerated profi'le fwhich would result from this Vertical only movement is shown in FIG. 2 and is referenced 138. It is important then that the roller move toward the position 137 to achieve a more symmetrical roll shape. To approximate the movement of the roller to the position 137, the bracket 133 is made to swing about an axis displaced forward of the cam 41 and wedge 43. In the machine described, this gives an approximate movement of the roller 41 to the position 137 'since in reality the roller should swing about a vcenter located directly below the axis of the trunnion'36 and spaced therefrom a distance equal to the. distance betweenlthe center of the roller 45 land the axis on which the cam 41 rotates. The location of the pivot of the bracket 133 below the trunnion 36 is impractical from the standpoint of f'abrication and assembly and the approximation described has been found satisfactory with no appreciable error involved.

The cam 41 as previously stated is rotated in response to the movement of the grinding wheel 37 along the roll 15. The drive to the cam 41 is supplied by a fluid motor 139, PIG. 8, which is connected to theshaft by a gear train including a pinion 140 on its output shaft 141, a step down gear 142 on an idler shaft 143 and va further step down gear 144 fixed directly to the shaft 55. The motor 139 is operated as a servo motor to rotatethe cam 41 in response to relative'movement of the grinding wheel 37 'and 'the cariage 26 along the roll 15. The control circuit for the motor 139'is shown schematically inFIG. 5. Thecircuit includes a transmitter synchro 145 located in a control cabinet 146 that is mounted on the carriage 26 adjacent to the swivel plate 27 and the mechanism supported thereon. The space between the cabinet 146 and the swivel plate 27 is the normal locationfor the machine operator who rides lalong with' the carriage 26V such as a resolver synchro having a rotor with two Wind'- ings in quadrature and two sta-tor wind-ings also in quad-` rature) `and lthe rotor of theV synchro 145 is driven in re'- sponse to the movement of the carriage 26. A precision igage the cam 41 properly While the grinding wheel is at rack 147 is attached to the bed 22 below'the carriage 26. A pinion 148 is engaged with the rack 147 and isjournalled for rotation in thecarriage 26- Therefor'e as the 'carriage 26 is moved, the `pinion 148 is rotated;4 A bevel gear drive 149, 150 from the pinion 148 rotates a shaft 151. The shaft 151 is connected through beveledV spur gears 152, 153 to drive a' gear 154 which mesh'es with and drives a gear 155 attachedzto the Vrotor shaft 1356 of the synchro 145. V

The` synchro 145 produces an electrical signal when Vits rotor -s driven and this signal is connected viaa cable 157 to a difierential synchro 158, also located 'in the 'control cabinet 146. The'synchro 1 58rhas a ,handwheel 159 connected to its rotor shaft 160 and the electrical signal from the transmitter synchro 145 is modified in accordance with the anguiar position ofthe handwheel 159. 'rhemodified i signal from the differential synchro 158 is connected via a cable 161 to a receiver synchro 162 which is mounted in the Wheelhead 35, as shown in FIGS. 6 and 8, and has its rotor driven in response torotation of the cam 4.1. i A shaft 163 extends from the receiver synchro 162 tofthe adjusting rod 67. A roller bearing bushing 164 is fixed to the end of the rod 67 and has a set of rollers 165 journalled therein and engaged With a fiat surface 166 vformed along the shaft 163. Other rollers v(not shown) are carried by the bushing 164-and these roll on the cylindrical surface of the shaft 163 at the same aXial locationv as the rollers 165 to hold the fiat surface 166 and rollers 7 `165 in constant contact. As the shaft 55 is rotated, the adjusting rod 67 is also rotated and the shaft 13 in turn is rotated by the torque transmitted from the rollers 155 acting on the flat surface 156-Thus the rotor of the receiver synchro 162 is rotated in unison With the cam 4-1.

Whenever the rotor of the receiver synchro 162 is not in a predetermined angular relation with the r-otor of the transmitter and differential synchros 145, 158, an electrical output is connected via a cahle 167 to an amplifier 168. The signal is vamplified and transm'itted to a servo valve 159 through a cable 170. The servo valve 109 is adapted to control the operation of the motor 139 to rotate the cam 41 and with it the shaft 55 and adjusting rod 67 in a direction such that the receiver synchro 162 is driven toward positional correspondence with the transmitter and differential synchros 145, 158. This tends 'always to reduce the signal from the receiver synchro 1.*52 to the amplifier 168.

The rotatonal input at the transmitter synchro 145 must correspond to the length of the roll to produce not less than one complete rotation of the cam 41 as the grinding wheel 37 moves along the full length of the roll 15. Therefore the gears 154'| and 155 are placed in the cabinet 14-6 in an accessible location and are readily changeable for other similar gears of different speed ratios such that by a proper selection, the transmitter synchro 145 can bc rotated a desired amount. Change gears and their use are well known in the machine tool industry and a full description of the gears and ratios is not included herein. The gears 154, 155 drive only a very small load and consequently can be small precision instrument type gears which are easly handled and exchanged with little effort and very little storagespace is needed for a great number of other similar gears to provide the required speed ratios.

The differential synchro 158 is utilized to select either a concave or convex camber shape for the roll 15. The hand-wheel 159 is rot'atable between two angular position's and in being so rotated will produce an electrical output -to the receiver synchro which results in the energization of the motor 139 to rotate the cam 41 through 180 degrees. Therefore, with the grinding wheel 37 at a known position along the roll 15, for example, at its center, the cam 41 is in contact with the roller 45 at either its most .or least eccentric point to produce either a concave or convex Shape, respectively, and by a simple rotation of the handwheel 159 from one position to the other, the cam 41 is rotated to change the profile shape to be produced from one to the other. The depth of the concave shape or the height of the convex shape, of course, depends upon the setting of the described indicia on the dal 78 and gear 82.

The wheelhead 35 is a rather large unit and with the described mechanism inside, it is quite heavy. In additlon a motor 171, FIG. 7 is mounted on top and this motor 171 is connected to rotate the spindle 172 to which the grinding Wheel 37 is attached. This motor 171 and its mounting structure 173 add considerable mass to the wheelhead 35. Therefore a set of counter-weight .Springs 174 are included in the wheelhead 35 and are compressed between the slide 34 and the 'top of the wheelhead 35. The springs 174 are received against a flanged bushng 175 at the top and this bushng 175 is attached to a ball ended member 176 that is pivotally received in a socket 177 fixed in the wheelhead 'to allow for an angular movement as the wheelhead 35 is tilted. Since the wheelhead 35 is'attached only the front end of the slide 34 by the trunmon 36, lateral forces fr-om external sources on the rear of the wheelhead might cause a tendency for the wheelhead to cock slightly during tilting. To prevent this, a pair of roller track surfaces 178, 179, FIG. 8, are

formed vertically in the wheelhead 35 and these surfaces are engaged forcibly by rollers 180, 181 that are mounted on angle brackets 182, 183 which are fixed to the slide 34 and ex-tend upward into the wheelhead 35. The con- 3 tinuous forcible contact of the rollers 180, 131 operates to prevent the rear of the wheelhead from swinging during the tilt by the described mechanisms although the feed mechanisms do not in themselves create laterally acting forces.

The carriage 26 of the machine can be traversed along the ways 24, 25 on the bed 22 by a hydraulic control circuit as shown schematically in FIG. 9. As handwheel 134 is fixed on the end of a shaft 185 that is journalled for rotation in a sleeve 106 which in turn is rotatably received in the control cabinet 146. A bevel gear 187 is fixed on the end of the shaft 135 and is in mesh with a beveled gear 138 that is rotatable in a bushng 189 rotatably received inside the cabinet 146. A plunger 190 is threaded into the bushng 189 and is received through the gear 188 in splined engagement therewith. Therefore, as the handwheel 134 is rotated, the plunger 190' is rotated and, due to its thread, is moved axially relative to the bushng 189. The plunger 190 is engaged at its outer end by a lever 191 pivotal about its center and engaged at its other end by a plunger 192 in a servo valve V193. The plunger' 192 is biased into contact with the lever 191 by a spring 194. As shown, a pressure fiuid supply line 195 extends from a pump 196 and connects fiuid under pressure to the center of the valve 193. When the plunger 192 is shifted in either direction from the. position shown, fiuid under pressure is connected to one or the other of a pair of fiuid lines 197, 198. A return pressure line 199 is connected to the valve 193 and when the plunger 192 is shifted, one of the lines 197, 198 not connected to pressure line 195 is connected to the return pressure line 199. The lines 197, 198 are connected to a controlV motor 205 which is operable one way and the other in correspondence with the pressure dilferential in the lines 203, 204 to rotate a shaft 206 on which a beveled gear 207 is fixed. The gear 207 drives a gear 208 on a shaft 210 and a gear 209 is fiXed to the other end thereof. The gear 209 drives a gear 211 on the end of a worm shaft 212 journalled in the carriage 26 and the worm shaft has a worm`213 fixed thereon and enga'ged with a worm rack 214 that is fixed to the bed 22 parallel to the ways 24, 25. The worm 213 is angularly disposed relative to the worm rack 214 and forms a smooth power transmission system commonly called a Sellers drive. Thus it can be seen that rotation of the handwheel 184 produces displacernent of the plunger 192 in the servo valve 193 and this in turn causes the connection of'fluid under pressure to operate the motor 205 which drives the carriage 26 along the ways 24, 25 through the reaction of the worm 213 and the fixed worm rack 214. Thedirection of movement of the carriage 26 depends on the direction of rotation of the handwheel 184. o

The servo drive of the carriage 26 has a mechanical feedback to the mechanical input and indicates to the operator the motion produced by rotation of the handwheel 184. The shaft 206 extends through the motor 205 and its other end is splined and slidably receives a clutch member 215 that drives the bushng 189 when the shaft 206 is rotated. The clutch 215 is held engaged with the bushng 189 by a shifter fork 216 connected to the plunger 201 in the valve 200. Thus, the bushng is caused to tend to follow the rotation of the gear 188 and the axial displacement of the plunger 190 is limited to a small amount relative to the bushng which isl suflicient to cause energization of the motor 205. The clutch 215 also has a gear 217 fixed thereon which drives a larger gear 218 fixed to a shaft 2,19 journalled in the control cabinet 146 the other end of which carries a bevel gear 220 'that drives another bevel gear 221 fiXed on the sleeve 185. The sleeve carries a pinon 222 in an eccentric i location such that it meshes with and rolls around a fixed internal gear 223. The. pinion 222 also meshes with .an internal gear 224 that forms part of a reversing plate 225 that is rotatably received over the handwheell shaft 185. The gear 224 hasa different number of teeth than the gear 223. Therefore. the plate 225 is rotated slowly as the motor 205 is operated to give a sirnulation of the amount of carriage movement accomplished in response to rotation of the handwheel 184. The plate 225l rotates relative to a block 226 on which a reversing lever 227 is pivotally attachecl.v VThe lever 227 is engagable by dogs 228 that are adjustably positionable ,aroundthe plate 225 to reverse the direction of movement -of the carriage 26 at preset points `as will be described subsequently.

The carriage 26 is movable under full power operation as well as under the manual control mode described in regard to the handwheel184. The power movement can be initiated by two methods. One method is by the operators raising the handle '229 connected to the lever 227 to swing the lever 227 from its operative position described. This movement of Vthe lever 227 produces movement of a push rod 230 and operates -a limit switch SLS in the control cabinet 146. Operation of the limit switch 8LS causesl energizationof a solenoid 2SOL as will' be described subsequently herein. The solenoid 2SOL can also be energized by' an electrical selector switch to be described later which'is the normal automatic mode since the reversing lever227 is not swung normally away from itsV operative position. The solenoid 2SOL when energized pushes a valve plunger 231 leftward in a valve 232 shown in PIG. 9. The fluid pressure 1ine1195 connects to the center of the valve 232 and with the plunger 231 shifted leftwar-d, the line 195 is connected to a line 233 which has been connected previously to the return line 199 that also connects to the valve V232 at each end thereof. The line 233 connects to the upper end of the plunger 201 in the valve 200 and pressure :in that line now causes the plunger 201 to shift downward from the position shown to disconnect lines 197 and 198 from lines 203, and 204 respectively. Thusthe servo valve 193 is ineffective atthis time.l The shifter forkV 216 also moves downwardjat the same time to disconnect the clutch 215 from the bushing 189 so that the voperation of the motor 205 will not now rotate the bushing 189. The reversing plate 225 continues to be rotated since the gear 217 remains in engagement with the gear 218.

The energization of fthe motor 205 at this time is under control of a reversing valve 234 from which a pair of fluid lines 235, 236 extend to connect with Vthe valve 200. With the Vplunger 201 downward as described,V .the lines 235 and236 are connected respectivelywith the motor opei'ating lines 203 and 204. A secondary pressure line 237 extends fromV the valve 232 where it connects around to plunger 241 in the position shown since a fluid line 252 from the rate valve 251 is connected directly to the secondary pressure line 237. The line 248 is at return pressure since ia line 253 from the rate valve 250 connects around the plunger -241 to a branch line 254 that connects with the main return line 199. Therefore the pressure differential on the ends of the plunger 238 is such that it remains as'shown. e

The plunger 241 in the pilot valve 240 is hydraulically detented to remain in a selected end position. An enlarged cylinder section 255 is formed in the valve 240 and apiston land 256 is formed on the plunger 241 which is slidable back and forth in thel cylinder section 255. The secondary pressure line 237 connects at the center of the cylinder section 255 and connects pressure only on one side or the other of the piston land 256 when the plunger 241 is in one or the other of its two end positions. As shown, the pressure from line 237 is connected tothe left side of the land 256 and the plunger 241 is held in its right end position.

The position of the plunger 241 can be'changed automatically as the carriage `26 is reciprocated between pre- 241 one way and the other in the valve 240. This automatic reversal by the dogs 228`occurs only when Vthe the mainpressure line 195. The line 237 connects to in the by-pass valve 244, in the position shown, blocks the line' 242 and therefore line 242 is connected only through the rate valve 243 to a line 246 connecting through the by-pass valve 244 around its plunger 245 to the main return line 1959. This causes energization of the motor 205 at a ratedetermined by aXial adjustment of a sleeve 247 in the valve 243 and in a direction corresponding to the position of the plunger 238 in the valve 234.

Theposition of the plunger 238 in the valve 234 is'controlled by the fluid pressure differential in apair of lines 248, 249 extending from a pair of rate valves 250, 251,

i respectively. i The line 249 is under pressure with. the

solenoid 2SOL is energized by the electrical switch, to be described, and not by the handle 229 since the latter means swings the lever 227 out of operative position. The described hydraulic detent mechanismoperates to hold the plunger in the position to which it is shifted. As shown, the dog 228 will swing the lever 227 counter-clockwise and the plunger 241'will shift to the left. The fluid pressure differential then is reversed'between lines 252 and 253 and therefore between lines 248 and 249 to reverse .the plunger 238 in the valve 234. This-reverses the fluid pressure connections to the lines 235 and 236 and consequently the motor 2,05 reverses and runs in the op.- posite direction to reverse the direction of carriage travel. The rate at which the plunger 238 is shifted depends upon the rate setting of the valve 251 since fluid ahead of the plunger 238 must escape through the, line 249 and the rate valve 251, whilefluid by-passes the rate valve 250 through a check valve 260. When the plunger 238 is shifted to the position; shown, its rate is 4controlled by the valve 250 and pressure fluid by-passes the'valve 251` .through a check valve 261. The rate valves 250, 251

from the line 237 toa line 264`that extends to a cylinder 265 on the end of the valve 240 and into which thelplunger 241extends. The plunger 241 hasa piston 266'formed thereon and slidable in the cylinder 265. Another line 267'between the valve 262 and the cylinder 265 at the other side of the piston is connected to the main return 199 at the valve 262. Therefore the plunger 241` tends to shift leftward. The area of'the piston 266 is slightly greater than the area of the detent piston 256 and consequently the plunger 241 doesshift leftwar'd as if the lever 259 had been turned to reverse the plunger position'. The solenoid 5SOL operates to Shift the plunger 263 in the reverse directionto connect a pressure difference between the fluid lines 264 and 267 to shift the line 199 as shown to enable the lever 259 to be swung easily to reverse the drive to the carriage 26.

The carriage 25 can be moved at' a rapid traverse rate by operation of the by-pass valve 244. A solenoid operated control valve 268 controls the connection of fluid under high and low pressure to a pair of operating lines 269, 270. The pressure line 195 is connected to the center of the valve 268 and with its plunger 271 in the position shown due to the bias of a spring 272, pressure is connected to the line 269. The secondary return line 254 is connected to the valve 268 at each end thereof and the line 270 is connected to the return pressure of line 254 at this same time. The resulting pressure difference holds the plunger 245 of the valve 244 as shown. When the Operating solenoid ISOL is energized, the plunger 271 is shifted leftward against the spring and the line 278 is connected to the pressure line 195 while the line 259 is connected to the main return line 199 and the plunger 245 is shifted to the left in the valve 244. Therefore the line 242, through which return fluid from the motor 205 passes, is connected in an unrestricted manner to the main return line 199 and the motor 205 operates at a high rate of speed to produce rapid movement of the carriage 26.

The circuit described in PIG. 9 operates the carriage by power in a completely hand Controlled mode as described with rotation of the handwheel 184. As also described, full power Controlled operation of the motor 205 is also available to produce either automatic reversal of the carriage through operation of dogs 258 and the lever 259 or by selected use of the valve 262 through energization of the solenoids 4SOL and SSOL. The rate of carriage movement can be set by the valve 243 or can be at a rapid rate due to the by-passing of the valve 243 when the solenoid ISOL is energized selectively.

The schematic hydraulic circuit for FIG. 10 operates the feed of the grinding wheel 37 toward and away from the roll by controlling the supply of fluid under pressure to the motors 38, 139 and 273 (PIG. 10), the latter being operable to produce power movement of the wedge 43 both in an automatic pick-feed mode and a manual control mode. A pair of fluid lines 274 and 275 FIG. 9, are connected, respectively, to the fluid lines 252 and 253 to provide fluid pressure signals at each reversal of the carriage 26 at the ends of the roll 15. The fluid lines 274, 275 each connect to a section of a pickfeed selector valve 276 which is shown rotated to the pickfeed position. With the valve 276 as shown, the fluid lines 274, 275 are each in communication with another line 277, 278, respectively, and these latter lines connect to the pickfeed control valve 279, FIG. 10. Upon a reversal of the pilot valve 240, FIG. 9, from the position shown, the fluid line 253 is connected to pressure and consequently the line 278 is pressurized. At this same time line 252 is at return pressure and line 277 is likewise at the same low pressure. A plunger 280 in the valve 279 is immediately shifted rightward from the position shown in PIG. 10 due to the pressure ditferential at its ends where the lines 277 and 278 are connected. The pressure fluid in the line 278 is also connected to a control valve 281 at its left end to move a plunger 282 therein rightward, vas viewed in FIG. 10. The fluid line 277 is connected to the right end of the valve 281 through a dynamic resistance 283 which controls the rate of movement of the plunger 282 since it restricts the flow of fluid to exhaust ahead of the plunger 282. When the plunger 282 has shifted part way toward its right end position in the valve 281, pressure from line 278 is connected to a line 284 which is in communication with a piston 285 in a cylinder 285 that drives a second piston 287 in a fluid meter cylinder 288. At this same time, the fiuid line 277 under low return pressure is connected around the plunger 282 to a fluid line 289 and the piston 285 moves rightward quickly pushing the piston 287 ahead of it until a rod 290 engages an adjustable stop 291.

The setting of the stop 291 determines the stroke of the meter piston 287 and thus determines the volume of fluid exhausted through a line 292 ahead of the advancing piston 287. The fluid line 292 is connected through the valve 279 to a fluid line' 293 that in turn connects to a solenoid operated valve 294 which, in the condition shown, allows the fluid from line 293 to pass to a line 295. The line 295 connects with a valve 296 that passes the fluid therefrom to a motor Operating line 297 which connects the fluid to operate the motor 273. Thus the metered fluid from the cylinder 288 is utilized to drive the motor 273 a predetermined amount dependent upon the setting of the stop 291. A second motor Operating line 298 connects through the valve 297 to a fluid line 299 extending to the solenoid valve 294 where it connects to a line 300 that passes the exhaust fluid from the motor 273 to a rate valve 301 that in turn passes the fiuid at a preset rate to the main return line 199. The rate valve 302 controls the rate of pickfeed operation of the motor 273.

The fluid circuit de-scribed also operates to produce a pickfeed operation of the motor 273 when the line 277 is connected to high pressure and line 278 is connected to low pressure. This occurs when the carriage 26 is at its other reversing point. In this other case, the plungers 280, 282 are shifted back to the position shown sinceV the fluid pressure diiferential on their ends is reversed. The line 289 is then connected to high pressure during the shift of the plunger 282 while the line 284 is at return pressure and therefore the piston 285 is shifted back to the leftward position shown and the same metered amount of fluid is forced out through the line 289 ahead of the piston 287. This fluid from line 289 is passed to the same line 293 and from there it passes to the motor 273 via the same lines as before to operate that motor an equal amount in the same direction.

As shown, the motor 273 rotates a shaft 302 on which a pinion 303 is fixed and engaged with a gear 304 that is slidably received on a splined shaft 305 and is held in driving engagement with a clutch 306 connected to the handwheel 46. The gear 304 is held against the clutch 306 by a spring-set plunger 307 that swings a shifter lever' 308 which is engaged with the gear 304 to slide it on the shaft 305. The pinion 47 is fixed to the splined shaft 305 and thus the drive from the motor 273 is transmitted to the screw 53 which shifts the wedge 43 to tilt the grinding wheel 37 inward toward the roll 15.

The motor'273 is also continuously operable under manual control by operation of a dial 309 on which a cam face 310 is formed to control the positions of a pair of valve plungers 311, 312 in the valve 296 and another valve 313, respectively. The face 310 of the dial 309 is shaped such that when the dial 309 is rotated from a reference position, the plungers 311, 312 are caused to shift in opposite directions. As shown, the dial 309 is in its reference position and the plungers 311, 312 are in their corresponding positions. The shift of the plunger 311 in either direction from the position shown results in a disconnection of the fluid lines 295, 299 from the motor Operating lines 297 and 298 to prevent pickfeed at this time. The main pressure supply line connects to the center of the valve 313 while the main return line 199 is connected to it at each end. The motor Operating lines 297, 298 are each connected around the plunger 311 to the valve 313 at ports which are blocked from both the pressure line 195 and the return line 199 whilethe plunger 312 is in the position shown. It can be seen that a shift of the plunger 312 in either direction will result in the connection ofthe motor lines 297, 298 such that a pressure dilferential is produced therein to cause the motor 273 to operate. The direction of the pressure ditferential and the direction of operation of the motor 273 depends upon the direction of shift of the plunger 312 and this is dependent upon the direction in which the dial 309 is normally rotated. Since one or the other of the motor lines is connected directly to r 13 the return line 199, the rate of operation of the motor 273 dependsiupon the amount of rotation of Vthe dial 309 since the cam face 310 has a uniform slope therearound from low to high points to produce a uniform shift of the plunger 312. i f

A valve 314 similar to the valve 313Vcontrols the operation of the coarse wheelhead positioning motor 38 .by which the slide 34 is positoned on the sub-slide 31. The pressure line 195 connects to the center and the return line 199 is connected at each end of the valve 314. The valve plunger 315 blocks the pressure and return lines 195, 199 from a pair of motor Operating lines 316, 317 when in the position shown. The plunger 315 is held in the position shown by a dial 318 having a cam face 319 similar to that of the dial 309. When the dial 318 is rotated in one or the other directions from the position shown, the plunger 315 is shifted in one or the other directions to connect a fluid differential across the motor 38 to cause it to rotate the screw 39 and to shift the slide 34. The rate of operation of 1the motor 38 also depends upon` the distance'that the plunger 315 'is shifted from the position shown.`

` The fluid cirucit of FIG. also includes a circuit portion by which the fine feed mechanism can be reset since the wedge 43 can be moved only through a limited stroke at which time it cannot produce'further fine infeed movement of the grinding Wheel 37. The reset is controlled by two solenoids, 9SOL`and 10SOL, which shift two valve plungers 320, 321, respectively, when energized. The plunger 321 isina valve 322 to which both the pressure and retum lines 195, 199 are connected and from which a single fluid line 324 extends to the clutch plunger 307. When the solenoid 10SOL is deenergized the plunger 321 is in the position shown and the'line 324 is connected to the'main return therebyallowing the spring biased plunger 307 to holdthe grear 304 and clutch 306 engaged so that the handwheel 46 is r-otated when the wedge 43 is shifted. Upon 'reset, the solenoid 10SOL is' energized and the plunger 321 is shifted to the right and fiuid under high pressure is connected t-o the line 324 to shift the plunger 307 against its bias causing it to swing thev lever 308 counter-clockwise. The gear 304 is disconnected 14 16LS (FIG. 10) is operated by a trip rod 330 extending rearwardly from the wedge 34 (see also FIG. 7) and the contacts 16LS-1, FIG. 11, are closed to complete a circuit causing an indicator light 11LT to be lighted. The machine operator then momentarily closes a switch 7SW to complete a circuit through a set of normally closed limit switch contacts 15LS-1 to energize a 'relay 19CR. The normally open contacts 19CR-1 close to latch the relay 19CR energized even though the switch 7SW is released. Other contacts 19CR-2, 19CR-3 are also closed to energize the solenoids 9SOL, 10SOL which operate the valves 294 and 322 as describedto reset the fine feed mechanism. When the fine feed is reset and the wedge 43 is fully retracted, the trip rod 330 engages a limitv switch 15LS (FIG. 10) and the contacts 15LS-1 are opened to deenergize the relay 19CR. The contacts 19CR-1, 19CR-2 and 19CR-3 are all opened and the solenoids9SOL and 10SOL' are deenergized. The wedge 43 is then reset in the fine feed mechanism.

The electrical control circuit which produces the power movement of the traversing carriage 26 contains the previously described solenoids 1SOL through 5SOL. The carriage 26 can be moved rapidly under power by the energization of the solenoids 1SOL and 2SOL simultaneously, the solenoidV ISOL Operating the fast rate valve 268, FIG. 9,.and the solenoid 2SOL Operating the power feed valve 232. The control lever 229 is lifted v by the operator to cause the rod 230 to operate the limit from the handwheel 46 but remainsrengaged with the i When this happens, the main pressure line 195'is poonnected to the fiuid line 299 and the. return line 199 is connected to the line 295. These lines 299 and 295 areV connected through the valve 296 to the lines 298 and 297 respectively.;as previously described in the pickfeed operation but in this case the fluid pressure difierential is reversed iso' that the motor 273 is operated in the reverse direction from that described in the pickfeed operation. Therefore the wedge 43 is returned to a reset condition 'andvthe 'grinding wheel 37 is swung awayjfrom the roll 15,. The coarse position motor is usedto bring the grind- 'ing wheel-37 into range |of the fine feed mechanism when it is reset.

i The'ener'gizaton of the solenoids 9SOL and 10SOL .as well as .the energization of the previously mentioned solenoidsrIlSOL, 2SOL, 4SOL land SSOL canjbest be described with reference to FIG. 11. The circuit of FIG. 411is energized from a source 325 of alternating current which is connected. across power lines 326, 327 when a master start switch 1SW is closed and latched. VPower is also applied'through a fuse-328V to a power line 329 to4 which each of the solenoid circuits is connected. The

solenoids are not energized, however, until certain relay contacts in the circuits for the these relays are connected between the power lines 326 and 327.' VWhen the wheelswitch SLS. The contacts SLS-l, FIG. 11, are then closed while the contacts 8LS-2 are opened. The relay 2CR is energized as a result and its contacts 2CR-1 through 2CR-4- are all closed to complete energizing circuits through both the .solenoids 1SOL and 2SOL to cause the previously described movement of the carriage 26 at a rapid rate. This movement continues within the range of travel =of thev carriage 26 until the lever 229 is released.

The normal power movement lof the carriage 26 is produced at the preselected rate determined by thersetting of the rate valve 243 when the solenoid 2SOL is energized without the solenoid ISOL being energized. This is accomplished by a momentary closng ofv the switch 2SW when the limit switch 8LS is not operated. A circuit is completed through the normally closed contacts 8LS-2 and the switches 38W, normally closed, and 2SW which energizes the relay 3CR. The contacts. 3CR-1 close to latch'the relay 3CR energized even though the switch 2SW is only momentarily closed. The contacts 3CR-2 and 3CR-3 also close to complete a circuit through the solenoid 2SOL which shiftsthe valve 232 as described to produce the power movement of the carriage 26 and it occurs with automatic reversal since the lever 227, FIG. 9, engages the dogs 228 since the lever 229 is not lifted. This power operation continues until therswitch 35W is opened at which time therelay 3CR is deenergized and its contacts 3CR-1 through 3CR-3 areopened. V

The carriage 26 can be selectively reversed byV the operator without the engagement of the lever 227 and dogs 228 by operation of the valve 262 by one or theother of the solenoids 4SOL and SSOL. A pair of switches 5SW and 6SW are provided, each in circuit with a relay 12CR and 13CR respectively. When the switch SSW is closed, the relay 12CR is energized and its contacts 12CR-1, 12CR-2 are closed to energize the solenoid 4SOL. In a similar manner, when the switch 65W is closed, the relay 13CR is energized to close its contacts 13CR-1 and 13CR-2 and the solenoidSSOL is then energized. Thus the machine operator can reverse the direction of travel of the carriage'26 prior to reversal by the dogs 228 by the operation of one or the other of the push-button switches 5SW -and 65W. i

The 'circuit of FIG. 11 also shows schematically the connection of the synchros 145, 158 and 162 in the servo adam/tes This portion of the circuit is energized when the switch 88W is latched closed and power from the lines 326, 32.7 is connected across a power supply unit 331 which Supplies the power for the 'synchros 145, 153 and lZ and the servo valve 169. The power from the supply unit 331 is connected via the lines 332, 333, 334 to a Vdistribution panel 359 in the control cabinet 146 where it is distributed to the various units. The synchros shown are of the resolver type and the stators are comprised of two windings each, 335 and 336, 337 and 338, and 339 and 340 spaced in quadrature in each of the three. A single rotor winding 341 and 342, respectively, of the two available is used in the transmitter and receiver synchros 145 and 162 while the differential synchro 158 uses both of the two rotor windings 343, 344 therein. The synchros 145, 153 and 162 are interconnected as shown. The rotor 341 in the synchro 145 is energized by a reference alternating voltage connected from the panel 351) via power lines 345 and 346 and a voltage is induced in each of the stator windings 335, 336 which are connected to energize the stator windings 337, 338 in the differential synchro 158. The voltage induced by the rotor 341 depends upon its angular position which is controlled by the instantaneous position of the carriage Ze as this information is fed back to the rotor 341 by means of the rack 147 and pinion 148. The stator windings 337, 338, induce voltages in the rotor windings 343, 344 of the synchro 158 depending upon their angular relationships and these induced signals are connected to the stator windings 339, 340 of the synchro 162. The relative angular relation of the stator windings 337, 338 and rotor windings 343, 344 can be changed by the handwheel 159 so that the phase of the output signal connected to the synchro 162 changes by 180` degrees to determine either a concave or convex camber Shape as previously described. The stator windings `335i, 343' induce a signal in the rotor Winding' 342 of the receiver synchro 162 which is connected through conductors 347, 348 to the panel 359 where the amplifier 168, PIG. 5, is located and the amplified signal is .then connected in push-pull form to the two transducer' windings 349, 355i of the servo valve 169 to control the operation of the motor 139 that drives both the camber cam 41 and the rotor winding 342. Thus the desired camber form is produced on the roll 15 by a mechanism the controls for which are located -entirely at the normal operatofs station at the control cabinet 146 adjacent the wheelhead 35 on the carriage 26 and all adjustments of the various feed mechanism are made at this one location.

While the invention has been described in connection with one form or embodiment thereof in a particular roll grinding machine, it is to be understood that the present disclosure is illustrative rather than restrictive and that changes and modifications may be resorted to without departing from the spirit of the invention or the scope of the claims which follow.

What 'is claimed is:

1. In a grinding machine having a` wheelhead pivotally attached at one end to a slide member and a grinding wheel rotatably supported on a spindle in the wheelhead and movable relative to a work supporting mechanism when the wheelhead is tilted about said one end, a compound feed mechanism comprising in combination:

(a) a cam received in the wheelhead for rotation about an axis, said cam having (1) a peripheral surface variably spaced from the axis about which said cam is rotatable,

(b) a wedge movable on the slide member below said cam,

(c) a roller received in contact between said wedge and, said cam,

(d) means reciprocally to move said wedge to tilt the wheelhead about said one end thereof, and

(e) means to wiatr; the cam about said axis to add a 16 component of tilt to the wheelhead independent of movement of said wedge.

2. The grinding machine mechanism of claim 1 where- (a) said cam is circular,

(b) the axis of rotation of said cam is eccentric relative to the center thereof, and

(c) means are provided with said cam selectively to adjustthe relative eecentricity of the axis of rotation of said cam.

3. The grinding machine mechanism of claim 2 where- (a) a shaft is rotatably journalled in the wheelhead,

(b) an adjusting slide is attached at one end of said shaft for movement transverse to the axis of rotation thereof, (c) said cam is fixed to said adjusting slide, (d) means are provided releasably to clamp said adjusting slide in a selected position on said one end of the shaft, and i (e) means are provided selectively to Shift said adjusting slide when said adjusting slide is unclamped to eccentrically located said cam on said shaft.

4. The grinding machine mechanism of claim 3 Where- (a) said shaft is 'hollow, (b) a rod is slidably received through said shaft and said rod includes i (1) a pair of parallel and flat surfaces inclined relative to the aXis of said shaft, (c) said adjusting slide is in engagement with said fiat surfaces of the rod, and (d) a screw mechanism is included in said shaft and selectively operable to Shift said rod theren when said cam and adjusting slide are unclamped, said flat surfaces adapted to force said adjusting slide to move transversely on said shaft when said rod is shifted in the shaft. g 5. The grinding machine mechanism of claim 1 wherein: o

(a) the axis of rotation of said cam is parallel to and spaced from the grinding wheel spindle, and

(b) said wedge member is movable on said slide member in a direction perpendicular to the axis of rotation of said cam.

6. The grinding machine mechanism of claim 5 wherein said roller is mounted to pivotally swing about a point spaced fromthe roller when the wheelhead is tilted.

7. The grinding machine mechanism of claim 5 where- (a) a bracket is included having one end pivotally attached to the slide member at a point spaced from the axis of rotation of said cam and said one end of the wheelhead, and

(b) said roller is rotatably mounted on saidbracket at the other end thereof and is received in contact between said cam and wedge member.

S. In a roll grinding machine having a wheelhead pivotally attached at one end to a slide member and a grinding wheel rotatably supported in the wheelhead and movable toward and away from a roll supporting mechanism when the wheelhead is variably tilted about said one end, the wheelhead and roll supporting mechanism being relatively movable to carry the grinding wheel along the roll supporting mechanism, a compound feed mechanism comprising in combination:

(a) a cam rotatably received in the wheelhead for rotation about an axis, said cam having (l) a peripheral surface variably spaced from the axis about which said cam is rotatable, (b) a wedge movable on the slide member below said cam, I

(c) a roller received in contact between said wedge and the peripheral surface of said cam, w

(d) means selectively to shift said wedge and tilt the i 17 wheelhead about said one end thereof tov produce fine feed of the grinding wheel, and

(e) means to rotate said cam selectively one way and the other about said axis thereof in response to relative movement of the grinding wheel along the roll supporting mechanism to produce a cambering feed of the grinding wheel.

9.-The grinding machine mechanism of claim 8 wherein the means to rotate said cam includes:

(a) a reversibly operable motor connected to said cam,

and i (b) electrical apparatus responsive to the relative movement of the grinding 'wheel along the roll supporting mechanism between predetermined locations and to the instantaneous angular position of said cam Vto produce an electrical signal to operate said motor for simultaneous rotation of said cam between angular positions corresponding to said predetermined relative locations of the grinding wheel and roll supporting mechanism.

10. The grinding machine mechanism of claim 8 where- (a) a shaft is supported and journalled in the wheelhead for rotation on its longitudinal axis,

(b) said cam is circular, v

(c) means are provided tovattach saidcam to said shaft with a relative eccentricity therebetween,

(d) a dial is included in said means to attach said cam to said shaft and indicates the relative eccentricity therebetween in terms of an amount of camber, and

(e) said means to rotate jsaid cam operates to rotate said shaft.

11. In a roll grinding machine having a wheelhead pivi 'otally attached to a slide, a grinding wheel rotatably supported in the wheelhead, a rotatable cam operable to lift one end of the wheelhead to swing the grinding wheel to camber a roll supported across the periphery of the grinding wheel, the grinding wheel' i being relatively reciprocally movable along the length of the roll, a cambering feed control mechanism comprising:

(a) a reversibly operable motor connected to rotate said cam when energized, and

(b) a control circuit responsive to the relative movement of the grinding wheel along the roll between the ends thereof and to the instantaneous angular position of said cam to produce an electrical signal to operate said motor for simultaneous rotation of said cam between angularpositions corresponding to the ends of the roll.

12. The grinding machine mechanism of claim 11 wherein the electrical control circuit includes:

(a) a transmitter synchro having a rotor reciprocally rotatable in response to relative reciprocation of the grinding wheel and the roll,

(b) a differential synchro electrically connected to the transmitter synchro and having arotor rotatable bei tween one -and the other of two positions when the grinding wheel is aligned at a preselected reference position along the roll,

(c) a receiver synchro electrically connected to said difierential synchro and having a rotor mechanically connected for rotation by said motor with said cam,

18 v (d) an amplifier electrically connected to said receiver synchro and operable to produce a signal when said transmitter and diiferential synchro rotors are each rotated to energize said motor to rotate said cam and receiver synchro rotor a corresponding amount,

(1) the cam rotating degrees when said difier-z ential synchro is'rotated from one of said two positions to the other thereby providing a coni cave and convex camber adjustment. 13. The grinding machine mechanism of claim 12 wherern: i

' (a) a set of exchangable pick-.off gears are connected to rotate said transmitter synchro rotor to effect not more than 360 degrees of rotation of the cam when the grinding wheel and roll are relatively moved the full length of the roll. p I

14. In a roll grinder having a grinding wheel rotatably supported in a wheelhead that is pivotally movable about one end to swing the grinding wheel toward and away from a roll that is relatively reciprocally movable along its length across the grinding Wheel, a cambering mechanism comprising in combination:

(a) a rotatable shaft, i

(b) means for rotating said shaft one way and the other in response to relative reciprocal movement 'of the grinding wheel along the length of the roll,

(c) an adjusting slide attached at one end of said shaft for movement transverse to the axis of rotation thereof,

(d) a cam fixed to said adjusting slide,

(e) a rotatable dial having camber dimensions scaled therearound, i i

(f) means responsive to rotation of said dial for shifting said adjusting slide to eccentrically locate said cam relative to said shaft,

(g) means for releasably clamping said adjusting slide in a selected position relative to said shaft, and

(h) means for alternately lifting and lowering the Wheelhead at the other end thereof to pivot it about said one end in response to rotation of said cam.

15. The roll grinder mechanism of claim 14 wherein:

(a) said shaft is hollow, i

(b) a rod is slidably received through said shaft an includes i (1) a pair of parallel and flat surfaces inclined relative to the axis of said shaft,

(c) said adjusting slide is in engagement With said flat surfaces of the rod, and

(d) a screw mechanism is connected between said rod and said dial and is rotatable in response to rotation of said dial to shift said rod axially in said shaft when said adjusting slide is unclamped, said inclined surfaces operable when the rod is axially shifted to force said adjusting slide to an adjusted position corresponding to rotation of said dial.

References Cited by the Examiner UNITED STATES PATENTS 2,l67,948 V8/39 Herfurth'et al. 51-95.1 2,254,020 8/41 Schulte et al 51-95.1

LESTER M. swINGLE, Primary Examiner. 

1. IN A GRINDING MACHINE HAVING A WHEELHEAD PIVOTALLY ATTACHED AT ONE END TO A SLIDE MEMBER AND A GRINDING WHEEL ROTATABLY SUPPORTED ON A SPINDLE IN A WHEELHEAD AND MOVABLE RELATIVE TO A WORK SUPPORTING MECHANISM WHEN THE WHEELHEAD IS TILTED ABOUT SAID ONE END, A COMPOUND FEED MECHANISM COMPRISING IN COMBINATION: (A) A CAM RECEIVED IN THE WHEELHEAD FOR ROTATION ABOUT AN AXIS, SAID CAM HAVING (1) A PERIPHERAL SURFACE VARIABLY SPACED FROM THE AXIS ABOUT WHICH SAID CAM IS ROTATABLE (B) A WEDGE MOVABLE ON THE SLIDE MEMBER BELOW SAID CAM, (C) A ROLLER RECEIVED IN CONTACT BETWEEN SAID WEDGE AND SAID CAM, (D) MEANS RECIPROCALLY TO MOVE SAID WEDGE TO TILT THE WHEELHEAD ABOUT SAID ONE END THEREOF, AND (E) MEANS TO ROTATE THE CAM ABOUT SAID AXIS TO ADD A COMPONENT OF TILT TO THE WHEELHEAD INDEPENDENT OF MOVEMENT OF SAID WEDGE. 